Heat exchanger, and heat pump comprising at least one heat exchanger.

Abstract

The object of the present invention is to provide an improved heat exchanger and an improved heat pump of the type described above, which require relatively little installation space and / or have improved efficiency. [Solution] At least one flow channel duct 8 is formed as a tubular conduit with a circular cross-section, and a plurality of rigid vortex imparters 9 fixed in place are inserted into the flow channel duct 8 as internal components, and each of the plurality of vortex imparters 9 has a central axis 10 in the middle portion that extends in the main flow direction 7 and a plurality of guide vanes 11 that extend radially outward from the central axis 10.

Description

Technical Field

[0001] The present invention relates to a heat exchanger. This heat exchanger has at least one longitudinally extending flow path duct, through which a fluid is passed in a main flow direction that coincides with the longitudinal direction of the flow path duct during operation. The present invention further relates to a heat pump provided with at least one such heat exchanger.

[0002] This type of heat exchanger is used, for example, in a heat pump system, and various embodiments are known in the prior art. In this case, various heat exchanger structures are used, for example, tube-type heat exchangers, multi-tube heat exchangers, finned tube-type heat exchangers, and plate-type heat exchangers. One drawback of these heat exchangers is that they occupy a large installation space. Also, at present, only low COP values (Coefficient of Performance) can be obtained by these means. The COP value represents the efficiency of the heat pump system. This indicates the ratio of the heat output to the operating energy required to achieve it, and this operating energy is supplied to the heat pump system in the form of electricity.

Summary of the Invention

Problems to be Solved by the Invention

[0003] Starting from this prior art, the object of the present invention is to provide an improved heat exchanger with a relatively small installation space and / or improved efficiency, and an improved heat pump of the type described at the beginning.

Means for Solving the Problems

[0004] To solve this problem, the present invention provides a heat exchanger of the type described at the beginning, characterized in that at least one flow channel duct has internal components and / or structural features that impart a circumferential vortex to the fluid flowing in the main flow direction within the flow channel duct. Research has shown that the fluid vortex generated by such intentionally induced vortices results in improved heat transfer intensity, particularly in the state of liquid, non-boiling, and non-gas fluids. Furthermore, it has been found that the added vortex can minimize pressure loss, particularly in the boiling state of the fluid. Therefore, given the same installation space, the efficiency of the heat exchanger according to the present invention can be optimized compared to a conventional heat exchanger in which the fluid flows only in the main flow direction through the flow channel duct. Alternatively, the installation space can be reduced for the same or improved efficiency.

[0005] According to a first embodiment of the present invention, at least one flow channel duct is formed as a tubular conduit with a circular cross-section, in which a plurality of fixed, rigid vortex imparters are inserted as internal components within the flow channel duct, each of which has a central axis in the middle extending in the direction of the main flow and a plurality of guide vanes extending radially outward from this central axis, and these guide vanes impart a desired vortex to the fluid flowing into each vortex imparter. It has been found that the heat transfer strength of a tubular conduit having such vortex imparters can be approximately twice that of a flow channel duct without vortex imparters.

[0006] According to another embodiment of the present invention, at least one elongated flow channel duct is formed as a tubular conduit, which is at least partially divided into at least two subducts extending parallel to each other in the main flow direction, with a partition wall extending between these subducts, and a baffle plate extending laterally with respect to the main flow direction provided downstream of the first subduct and upstream of the second subduct, the partition wall being provided with a plurality of fluid flow openings, and fluid introduced into the first subduct is guided to the second subduct through these fluid flow openings. The forced direction change of this fluid from the first subduct to the second subduct, mainly brought about by the baffle plate and the plurality of fluid flow openings in the first subduct, accurately imparts a circumferential vortex flow to the fluid in the flow channel duct. By configuring at least one flow path duct in this way, the heat transfer intensity of the heat pump system can be increased by up to five times compared to conventional heat exchangers that pass fluid through simple tubular conduits with a circular cross-section, which allows for a particularly significant reduction in installation space.

[0007] At least one elongated flow channel duct is divided at least partially into three subducts that extend parallel to each other in the main flow direction, with a partition wall extending between each of them. A baffle plate extending laterally to the main flow direction is provided downstream of the first central subduct and upstream of the second and third subducts, respectively. These partition walls are provided with multiple fluid passage openings, and the fluid introduced into the first subduct is guided through these fluid passage openings, experiencing vortices, to the second and third subducts. This structure allows for the maximum increase in heat transfer intensity compared to conventional heat exchangers that pass fluid through simple tubular conduits with a circular cross-section.

[0008] Preferably, the first partial duct has a rectangular, preferably square, cross-section, and the second and third partial ducts each have a semicircular cross-section. This structure has proven to be particularly simple, inexpensive, and efficient.

[0009] The baffle plate of the first partial duct is provided with at least one through-hole, or preferably at least one through-slit. Such multiple through-holes and / or multiple through-slits make it possible to minimize friction loss in particular.

[0010] It is preferable that multiple fluid flow openings are spaced apart from each other in the main flow direction, and the distance between adjacent fluid flow openings preferably increases gradually downstream. This also helps to reduce flow losses.

[0011] According to another embodiment of the present invention, a plurality of flow channel ducts are provided, each flow channel duct is formed of a plurality of linear flow channel sections extending in the direction of the main flow and connected to one another via a plurality of fluid flow openings, these flow channel sections overlap each other in the direction of the main flow and are offset from each other in the direction of the main flow, in which case each flow channel duct through which a high-temperature fluid passes preferably has contact with an adjacent flow channel duct through which a low-temperature fluid passes along its entire length. Because the individual flow channel sections connected to each other via a plurality of fluid flow openings are thus overlapping each other in the direction of the main flow and offset from each other in the direction of the main flow, the effect is produced that the fluid passing through the flow channel duct receives a circumferential vortex flow as it moves from one flow channel section to the next. In several tests concerning the increase in heat transfer intensity, such a structure yielded the best results, up to 7 times better than conventional heat exchangers through which the fluid passes through tubular conduits with a circular cross-section.

[0012] The aforementioned flow channel duct section is formed by a plurality of rectangular parallelepiped hollow rods, each having a square end face, with each free end of these end faces having a single fluid flow opening. In this way, a simple modular structure is achieved. These hollow rods can be connected to each other, for example, by material bonding. However, these hollow rods can also be manufactured together by additive manufacturing, in which case the individual hollow rods exist only virtually and not in reality.

[0013] These fluid passage openings are preferably formed in a slit shape, in which case it is advantageous if the slit width is 0.1 to 0.3 times, particularly 0.25 times, the length of the end face of the hollow rod. In this way, friction loss can be minimized.

[0014] According to another embodiment of the present invention, the heat exchanger is in the form of a finned plate heat exchanger, which has a plurality of flow channel ducts, each of which is partitioned by two parallel plates and a plurality of fins arranged at an angle, and has a trapezoidal cross-section, in which case a plurality of fluid flow openings are provided in at least one end wall of each flow channel duct, and fluid introduced into one flow channel duct is guided into adjacent flow channel ducts through these fluid flow openings, while being subjected to circumferential vortices in the flow channel duct.

[0015] Preferably, each of the multiple fluid passage openings (15) is provided with a hood (27) that opens towards the inflow side, on the side through which the fluid is introduced into the flow channel duct (8). These hoods can be manufactured, for example, by slitting and deforming a sheet that forms fins, thereby achieving a very simple structure.

[0016] The present invention further provides a heat pump comprising at least one heat exchanger according to the present invention.

[0017] Further advantages and features of the present invention will become apparent from the following description with reference to the accompanying drawings. [Brief explanation of the drawing]

[0018] [Figure 1] Schematic diagram of a heat pump. [Figure 2] A perspective view of a flow duct formed according to a first approach of the present invention is shown. This flow duct can be the flow duct of the heat exchanger of the heat pump shown in FIG. 1. [Figure 3] An enlarged side view of the vortex generator shown only schematically in FIG. 2. [Figure 4] A graph showing the improvement in heat transfer intensity of the modified example of the flow duct shown in FIG. 2 with respect to the reference flow duct as a function of the Reynolds number. [Figure 5] A graph showing the increase in flow friction loss of these modified examples with respect to the reference flow duct as a function of the Reynolds number. [Figure 6] A graph showing the improvement in heat transfer intensity of these modified examples with respect to the reference flow duct when the Reynolds number is 10,000. [Figure 7] A perspective view of a first modified example of a flow duct formed according to a second approach of the present invention is shown. This flow duct can be the flow duct of the heat exchanger of the heat pump shown in FIG. 1. [Figure 8] A perspective view of a second modified example of a flow duct formed according to a second approach of the present invention is shown. This flow duct can be the flow duct of the heat exchanger of the heat pump shown in FIG. 1. [Figure 9] A perspective view of a third modified example of a flow duct formed according to a second approach of the present invention is shown. This flow duct can be the flow duct of the heat exchanger of the heat pump shown in FIG. 1. [Figure 10] A perspective view of the first modified example shown in FIG. 7 is shown, and this modified example shows, as an example, the direction change of the fluid guided through its flow duct. [Figure 11] A graph showing the improvement in heat transfer intensity of the modified examples illustrated in FIGS. 7 to 9 with respect to the reference flow duct as a function of the Reynolds number. [Figure 12]Graph showing the increase in flow friction loss with respect to the reference flow path duct of the modification examples shown in FIGS. 7 to 9 as a function of the Reynolds number. [Figure 13] Graph showing the improvement in heat transfer intensity with respect to the reference flow path duct of the modification examples shown in FIGS. 7 to 9 when the Reynolds number is 10,000. [Figure 14] Perspective view of a heat exchanger that can be the heat exchanger of the heat pump shown in FIG. 1. These flow path ducts are formed according to the third approach of the present invention. [Figure 15] Cross-sectional view along line XV of FIG. 14. [Figure 16] Perspective view of the heat exchanger shown in FIG. 14, partially shown in perspective. [Figure 17] Schematic diagram of two flow path ducts of the heat exchanger shown in FIG. 14. [Figure 18] Graph showing the improvement in heat transfer intensity with respect to the reference flow path duct of three modification examples of the flow path duct shown in FIG. 17 as a function of the Reynolds number. [Figure 19] Graph showing the increase in flow friction loss with respect to the reference flow path duct of three modification examples of the flow path duct shown in FIG. 17 as a function of the Reynolds number. [Figure 20] Graph showing the improvement in heat transfer intensity with respect to the reference flow path duct of three modification examples of the flow path duct shown in FIG. 17 when the Reynolds number is 10,000. [Figure 21] Perspective view of a first modification example of a flow path duct formed according to a first modification example of the fourth approach of the present invention. This flow path duct can be the flow path duct of the heat exchanger of the heat pump shown in FIG. 1. [Figure 22] Front view of the flow path duct shown in FIG. 21, showing the direction change of the fluid guided through this flow path duct. [Figure 23] Perspective view of a second modification example of a flow path duct formed according to the fourth approach of the present invention. This flow path duct can be the flow path duct of the heat exchanger of the heat pump shown in FIG. 1. [Figure 24]Figure 23 is a front view of the flow channel duct, illustrating the change in direction of the fluid guided through this duct. [Figure 25] A perspective view of a third modified example of a flow channel duct formed according to a fourth approach according to the present invention is shown. This flow channel duct can be used as a flow channel duct for the heat exchanger of the heat pump shown in Figure 1. [Figure 26] Figure 25 is a front view of the flow channel duct, illustrating the change in direction of the fluid guided through this duct. [Figure 27] Graphs showing the improvement in heat transfer intensity for the modified configurations shown in Figures 21, 23, and 25 relative to the standard flow channel duct, as a function of the Reynolds number. [Figure 28] Graphs showing the increase in flow friction loss as a function of the Reynolds number for the modified examples shown in Figures 21, 23, and 25 relative to the standard flow channel duct. [Figure 29] Graphs showing the improvement in heat transfer intensity for the modified versions shown in Figures 21, 23, and 25 relative to the standard flow channel duct, when the Reynolds number is 10,000. [Figure 30] A graph showing the improvement in heat transfer intensity of a flow channel duct configured according to four approaches according to the present invention, as a function of the Reynolds number, compared to a reference flow channel duct. [Figure 31] A graph showing the increase in flow friction loss of a flow channel duct configured according to the four approaches of the present invention, compared to a reference flow channel duct, as a function of the Reynolds number. [Figure 32] A graph showing the improvement in heat transfer intensity of a flow channel duct configured according to four approaches according to the present invention compared to a reference flow channel duct, when the Reynolds number is 10,000. [Figure 33] Perspective views illustrating a conventional heat exchanger and a heat exchanger modified according to the present invention. In the following text, the same reference numerals indicate the same or the same type of component or component region. [Modes for carrying out the invention]

[0019] Figure 1 schematically shows a heat pump 1, which has a first heat exchanger 2, a compressor 3, a second heat exchanger 4, and a throttle valve 5, all of which are connected in series to a fluid circulation circuit 6 through which a fluid in the form of a refrigerant is passed. In the first heat exchanger 2, energy is extracted from a naturally supplied heat source (e.g., air, water, or soil), and this energy is sent to the fluid refrigerant, causing it to evaporate. Next, this refrigerant is sent in vapor form to the compressor 3, which then sends the compressed refrigerant to the second heat exchanger 4. In the second heat exchanger 4, the refrigerant is condensed, and in this case, the energy extracted from the refrigerant is transferred to a fluid to be heated, such as heating water, which is then heated. Finally, the refrigerant is supplied to the throttle valve 5 to expand and then returned to the first heat exchanger 2.

[0020] In conventional heat exchangers 2 and 4, regardless of whether they are constructed as tubular, multi-tube, finned-tube, or plate heat exchangers, the fluid is guided linearly in the main flow direction 7 through at least one longitudinally elongated flow channel duct 8, in which case the main flow direction 7 coincides with the longitudinal direction of the flow channel duct 8. The present invention is based on the fundamental concept of providing at least one flow channel duct 8 with internal components and / or structural features that impart circumferential vortices to the fluid flowing in the main flow direction 7. The objective is to thus increase the intensity of heat transfer and / or reduce the required installation space of the heat exchangers 2 and 4.

[0021] Figures 2 and 3 illustrate a first approach according to the present invention, in which two vortex generators 9 are inserted into a flow channel duct 8 as internal components. The flow channel duct 8 is a tubular conduit with a smooth inner surface and a circular cross-section of diameter D. These vortex generators 9 are rigidly inserted into the flow channel duct 8 in a fixed position, and each comprises a single central axis 10 extending to the center of the main flow direction 7, and a plurality of guide vanes 11 extending radially outward from this central axis 10, which impart circumferential vortices to the fluid flowing through the vortex generator 9 in the main flow direction 7. For this purpose, the guide vanes 11 in this example are formed in an arc shape, and the angle α between the main flow direction 7 and the tangent 12 at the downstream edge of the guide vane 12 is preferably 60°. This angle α, as well as the number of guide vanes 11, which is eight in this example, can be changed in principle.

[0022] According to the first test, under the following conditions, the total fluid mass flow rate m t The fluid was flowed through the flow channel duct 8 shown in Figure 2. Fluid: Air (ideal gas) Inlet pressure p* in = 1 atm Inlet temperature T* in =303.15K External temperature T h =373.15K External heat transfer coefficient (HTC) h Reynolds number Re = variable Nusselt number Nu based on hydraulic diameter and friction coefficient f

[0023] In the first measurement series, the vortex-generating elements 9 were arranged at intervals of L=6D.

[0024] In the second measurement series, the vortex-generating elements 9 were arranged at intervals of L=40D.

[0025] Under similar conditions, a reference measurement was performed using the same flow channel duct 8, but without placing the vortex generator 9 inside. This reference measurement is indicated by index 0.

[0026] Figures 4-6 show the results obtained in these experiments.

[0027] As shown in Figures 4 and 6, by installing vortex generators 9 in the flow channel duct 8, it is possible to increase the heat transfer intensity in the flow channel duct 8 by 1.5 to 4 times compared to the reference measurement value, depending on the Reynolds number, while simultaneously increasing the hydraulic loss by 2 to 8 times (see Figure 5). A decrease in the distance L between the two vortex generators 9 results in an increase in heat transfer intensity and an increase in hydraulic loss.

[0028] Figures 7-9 show modified flow channel ducts 8 formed according to a second approach according to the present invention, which are divided at least partially into a plurality of partial ducts 8a, 8b, and 8c, three in this example, that extend parallel to each other in the main flow direction 7, with partition walls 13 between each of these partial ducts. The first, central partial duct 8a of the illustrated flow channel duct 8 has a square cross-section. The other two partial ducts 8b and 8c adjacent to the central partial duct 8a each have a semicircular cross-section.

[0029] The geometric shapes of the modified flow channel duct 8 shown in Figures 7-9 are basically identical.

[0030] In the first modified form of the flow duct 8 shown in Figure 7, which is represented by the number "1" in Figures 11-13, a completely closed baffle plate 14 extending laterally with respect to the main flow direction 7 is provided downstream of the first central partial duct 8a, and upstream of the second partial duct 8b and the third partial duct 8c, respectively. Furthermore, the partition wall 13 is provided with a plurality of fluid flow openings 15, and the fluid introduced into the first partial duct 8a is guided through these openings, experiencing vortex flow, into the second partial duct 8b and the third partial duct 8c. In the illustrated embodiment, the spacing between the individual fluid flow openings 15 in the main flow direction 7 increases downstream. This geometric shape is hereafter indicated by index 1.

[0031] The geometric shape of the second modified form of the flow channel duct 8 shown in Figure 8, which is represented by the number "2" in Figures 11-13, is substantially the same as the portion of the flow channel duct 8 shown in Figure 7. However, the baffle plate 14 that closes the first central portion of the duct 8a is provided with a central circular through-hole 16.

[0032] The geometric shape of the third modified form of the flow channel duct 8 shown in Figure 9, which is represented by the number "3" in Figures 11-13, differs from the geometric shape of the flow channel duct 8 shown in Figure 8 in that the baffle plate 14 closing the first central portion duct 8a does not have a central through-hole 16, and instead has two horizontal through-slits 17 located in the upper and lower regions of the baffle plate 14.

[0033] In the second test, under the same conditions as in the first test, the total fluid mass flow rate was transmitted through the flow channel duct 8 shown in Figures 7-9.

[0034] Figure 10 shows how the fluid passing through the fluid passage opening 15 is subjected to circumferential vortices in the flow channel duct 8, as indicated by the arrows. The fluid velocity is maximum in the arc-shaped outer regions of the second and third partial ducts 8b and 8c.

[0035] Figures 11-13 show excerpts of the results obtained in these measurement series. Here again, a simple tubular conduit was used as the reference and assigned index 0.

[0036] As shown in Figures 11 and 13, the geometric shapes of Modifications 1 to 3 can increase the heat transfer intensity in the flow channel duct 8 by 4 to 10 times depending on the Reynolds number compared to the reference geometric shape 0, while simultaneously increasing the hydraulic loss by 40 to 100 times (see Figure 12). Providing one through-hole 16 or multiple through-slits 17 in the baffle plate 14 closing the first partial duct 8a significantly reduces the hydraulic loss and simultaneously slightly decreases heat transfer (see Figures 11 and 12).

[0037] Figures 14-17 illustrate a third approach according to the present invention for increasing heat transfer intensity. The illustrated heat exchangers 2 and 4 have a fluid inlet 18 and a fluid outlet 19 for a first fluid and a fluid inlet 20 and a fluid outlet 21 for a second fluid, which, in this example, are introduced in a countercurrent manner through the heat exchangers 2 and 4. For this purpose, a number of flow channel ducts 8 are provided, arranged in a matrix in cross-section (see Figure 15), in which case each flow channel duct 8 is formed by a number of linear flow channel duct sections extending in the main flow direction and connected to each other via a number of fluid flow openings 22, where these flow channel duct sections overlap each other in the main flow direction 7 and are offset from each other in the lateral direction with respect to the main flow direction 7. In this example, the individual flow channel duct sections of one flow channel duct 8 are arranged such that the flow channel duct 8 as a whole has a helical shape in its longitudinal direction. In this case, as shown on the left side of Figure 17, each flow channel duct 8 through which the high-temperature fluid flows preferably contacts an adjacent flow channel duct 8 through which the low-temperature fluid flows along its entire length. That is, the two flow channel ducts 8 are each "twisted" in a spiral shape. Each of these flow channel duct sections is formed by a cubic hollow rod 23 having square end faces in this case, and these end faces are provided with one fluid flow opening 15 at each free end. In this example, each of these fluid flow openings 15 is formed in a slit shape and extends in the main flow direction 7. Here, the slit width b is preferably 0.1 to 0.3 times, particularly 0.25 times, the length d of the end face of the hollow rod 23. By arranging the individual flow channel duct sections to overlap each other in the main flow direction 7 and to offset each other laterally with respect to the main flow direction 7, the fluid flowing through the flow channel ducts 8 is subjected to circumferential vortices, as shown by the dashed line 24 in Figure 17. These illustrated flow channel ducts 8 can be composed of individual hollow rods that are connected to one another, for example, welded or brazed together. However, instead, this matrix configuration can also be made by additive manufacturing, in which case these hollow rods are simply virtual hollow rods.

[0038] In the third test, the total fluid mass flow rate was applied through the flow channel duct shown in Figures 14-17 under the same conditions as in the first test. Here again, a simple tubular conduit was used as the reference and assigned index 0.

[0039] In the first modification, represented by the number "1" in Figures 18-20, the slit width b of the fluid passage opening in the hollow rod was 0.25 times the length d of the end face of the hollow rod; in the second modification (number "2"), it was 0.5 times; and in the third modification (number "3"), it was 1 time.

[0040] Figures 18-20 show excerpts of the results obtained in these studies.

[0041] As shown in Figures 18 and 20, the geometric shapes of Modifications 1 to 3 can increase the heat transfer intensity in the flow channel duct 8 by 4 to 7 times compared to the reference shape 0, depending on the Reynolds number, and in this case, the hydraulic loss increases by 20 to 45 times at the same time (see Figure 19). In this case, the geometric shape with the smallest slit width b increases both intensity and friction the most. In particular, the increased friction can be further significantly optimized by optimizing the geometric shape of the flow channel duct 8.

[0042] Figures 21-26 illustrate a third approach according to the present invention for increasing heat transfer intensity in a finned plate heat exchanger. Figures 21, 23, and 25 show three variations of a flow channel duct having largely the same geometric shape, which is partitioned by two parallel plates 25 and diagonally arranged fins 26, each having a trapezoidal cross-section. In the first variation shown in Figure 21, each fin 26 of one flow channel duct 8 is provided with a plurality of fluid flow openings 15, and fluid introduced into the flow channel duct 8 through these openings flows into adjacent flow channel ducts 8 in a swirling motion (see Figure 22). These fluid flow openings 15 are each provided with a hood 27 formed on the side from which the fluid is introduced into the flow channel duct 8, which is open to the inflow side, and in this example is manufactured by slitting and deforming the sheet forming the fin 26. In the second modification shown in Figure 23, multiple fluid flow openings 15 are provided on both fins 27 of one flow duct 8, in which case these hoods 27 are selected so that fluid introduced from one flow duct 8 to an adjacent flow duct 8 is then guided back to the next flow duct 8 (see Figure 24). In the third modification shown in Figure 25, multiple fluid flow openings are provided on both fins 26 of one flow duct 8, in which case these hoods 27 are selected so that fluid is introduced from two flow ducts 8 to a third flow duct 8 located between them (see Figure 26).

[0043] In the fourth test, the total fluid mass flow rate was applied through the flow channel ducts shown in Figures 21, 23, and 25, under the same conditions as in the first test. Here again, a simple tubular conduit was used as the reference and assigned index 0.

[0044] Figures 27-29 show excerpts of the results obtained in this study, where the numbers "1," "2," and "3" represent different variations.

[0045] The geometric shapes of modifications 1 to 3 allow the heat transfer intensity in the flow channel duct 8 to be increased by 2.5 to 7 times compared to geometric shape 0 (reference), depending on the Reynolds number, as shown in Figures 27 and 29. In this case, the hydraulic loss also increases by 1.8 to 2.5 times (see Figure 28). In this case, the best result was obtained with the geometric shape of the second modification.

[0046] Figures 30-32 show a relative comparison of approaches 1-4, represented by the numbers "1"-"4". In summary, the second approach proved to be very promising because it resulted in the greatest increase in heat transfer intensity. A major advantage of this second approach, like the first and fourth approaches, is that it can be implemented relatively easily in existing heat exchanger structures and can be retrofitted as needed. As an example, Figure 33 shows conventional heat exchangers 2 and 4 on the left, whose flow path duct 8 is formed by simple, smooth, circular tubular conduits, and on the right, heat exchangers 2 and 4 modified according to the second approach, in which case the structural volume is significantly reduced while maintaining equivalent heat transfer intensity.

[0047] Figure 32 compares the heat transfer intensity of three approaches when the Reynolds number is 10,000. In the case of the third approach, the increase in heat transfer intensity is smaller than in the case of the second approach, but the optimization potential is maximized in the third approach. However, the third approach cannot be implemented with existing heat exchangers. Technically implementing the third approach requires the configuration of novel heat exchangers 2 and 4.

[0048] Although the present invention has been illustrated and described in detail with respect to several embodiments shown in the drawings, the present invention is not limited to the disclosed embodiments, and other modifications can be derived therefrom by those skilled in the art without departing from the scope of protection defined by the appended claims of the present invention. In particular, it should be noted that the heat exchanger according to the present invention can be advantageously used not only in heat pumps but also in other art fields.

Claims

1. A heat exchanger (2, 4) having at least one vertically elongated flow channel duct (8), particularly a tubular heat exchanger, a tube bundle heat exchanger, a finned tubular heat exchanger and a plate heat exchanger (2, 4), During operation, the fluid flows through the main flow direction (7) which coincides with the longitudinal direction of the at least one flow path duct (8). The at least one flow channel duct (8) has internal components and / or structural features that impart vortices to the fluid flowing in the main flow direction (7) in the circumferential direction of the at least one flow channel duct (8), A heat exchanger characterized by (2, 4).

2. A heat exchanger (2, 4) according to claim 1, The at least one flow channel duct (8) is formed as a tubular conduit with a circular cross-section, Multiple rigid vortex-generating bodies (9) fixed in place are inserted within the flow channel duct (8) as an internal component, and each of the multiple vortex-generating bodies (9) has a central axis (10) in the middle portion that extends in the main flow direction (7) and multiple guide vanes (11) that extend radially outward from the central axis (10). A heat exchanger characterized by (2, 4).

3. A heat exchanger (2, 4) according to claim 1 or 2, The at least one vertically elongated flow channel duct (8) is formed as a tubular conduit, and the at least one vertically elongated flow channel duct (8) is at least partially divided into at least two partial ducts (8a, 8b) that extend parallel to each other in the main flow direction (7). A partition wall (13) extends between these partial ducts, and a baffle plate (14) is provided downstream of the first partial duct (8a) and upstream of the second partial duct (8b), extending laterally with respect to the main flow direction (7). The partition wall (13) is provided with a plurality of fluid passage openings (15), and the fluid introduced into the first partial duct (8a) is guided through the plurality of fluid passage openings (15) to the second partial duct (8b). A heat exchanger characterized by (2, 4).

4. A heat exchanger (2, 4) according to claim 3, The at least one vertically elongated flow channel duct (8) is at least partially divided into three subducts (8a, b, c) that extend parallel to each other in the main flow direction (7). A partition wall (13) extends between them, and a baffle plate (14) is provided extending laterally with respect to the main flow direction (7) downstream of the first central partial duct (8a) and upstream of the second partial duct (8b) and the third partial duct (8c), respectively. The partition wall (13) is provided with a plurality of fluid flow openings (15), and the fluid introduced into the first partial duct (8a) is guided through the plurality of fluid flow openings (15) to the second partial duct (8b) and the third partial duct (8c) while being subjected to vortex flow. A heat exchanger characterized by (2, 4).

5. A heat exchanger (2, 4) according to claim 4, The first partial duct (8a) has a rectangular or preferably square cross-section, and the second and third partial ducts (8b, c) each have a semicircular cross-section. A heat exchanger characterized by (2, 4).

6. A heat exchanger (2, 4) according to any one of claims 3 to 5, The baffle plate (14) of the first partial duct (8a) is provided with at least one through hole (16), or preferably at least one through slit (17). A heat exchanger characterized by (2, 4).

7. A heat exchanger (2, 4) according to any one of claims 3 to 6, The plurality of fluid passage openings (15) are spaced apart from each other in the main flow direction (7), and the distance between adjacent fluid passage openings (15) gradually increases towards the downstream direction. A heat exchanger characterized by (2, 4).

8. A heat exchanger (2, 4) according to any one of claims 1 to 7, Multiple flow channel ducts (8) are provided, and each of the multiple flow channel ducts (8) extends in a linear main flow direction (7) and is connected to one another via multiple fluid flow openings (22), forming multiple flow channel duct sections, the flow channel sections overlap each other in the main flow direction (7) and are offset from each other in the lateral direction with respect to the main flow direction (7). Each of the plurality of flow channel ducts (8) through which the high-temperature fluid passes preferably has contact with an adjacent flow channel duct (8) through which the low-temperature fluid passes, along its entire length. A heat exchanger characterized by (2, 4).

9. A heat exchanger (2, 4) according to claim 8, The flow channel duct section is formed by a plurality of rectangular parallelepiped hollow rods (23) having square end faces, and each free end of the end face is provided with one fluid flow opening (22). A heat exchanger characterized by (2, 4).

10. A heat exchanger (2, 4) according to claim 9, The fluid passage opening (22) is formed in a slit shape and extends in the main flow direction (7), and its slit width (b) is 0.1 to 0.3 times, particularly 0.25 times, the length (d) of the end face of the hollow rod (23). A heat exchanger characterized by (2, 4).

11. A heat exchanger (2, 4) according to claim 1, which takes the form of a finned plate heat exchanger, and has a plurality of flow path ducts (8), Each of the plurality of flow channel ducts (8) has a trapezoidal cross-section partitioned by two parallel plates (25) and diagonally arranged fins (26), and each of the flow channel ducts (8) is provided with a plurality of fluid flow openings (15) in at least one end wall. A heat exchanger characterized by (2, 4).

12. A heat exchanger (2, 4) according to claim 11, On the side into which the fluid is introduced, each of the plurality of fluid passage openings (15) is provided with a hood (27) having an opening on the inflow side. A heat exchanger characterized by (2, 4).

13. A heat pump (1) comprising at least one heat exchanger (2, 4) according to any one of claims 1 to 12.

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